EP0423755A2 - Solenoid operated valve, especially for motor vehicle antilocking systems - Google Patents

Solenoid operated valve, especially for motor vehicle antilocking systems Download PDF

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Publication number
EP0423755A2
EP0423755A2 EP90119905A EP90119905A EP0423755A2 EP 0423755 A2 EP0423755 A2 EP 0423755A2 EP 90119905 A EP90119905 A EP 90119905A EP 90119905 A EP90119905 A EP 90119905A EP 0423755 A2 EP0423755 A2 EP 0423755A2
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EP
European Patent Office
Prior art keywords
valve
actuator
inlet
housing
valve according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP90119905A
Other languages
German (de)
French (fr)
Other versions
EP0423755B1 (en
EP0423755A3 (en
Inventor
Kurt Mohr
Gerhard Hahn
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ZF International UK Ltd
Original Assignee
Lucas Industries Ltd
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Filing date
Publication date
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Publication of EP0423755A2 publication Critical patent/EP0423755A2/en
Publication of EP0423755A3 publication Critical patent/EP0423755A3/en
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Publication of EP0423755B1 publication Critical patent/EP0423755B1/en
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Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/36—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition including a pilot valve responding to an electromagnetic force
    • B60T8/3615—Electromagnetic valves specially adapted for anti-lock brake and traction control systems
    • B60T8/363—Electromagnetic valves specially adapted for anti-lock brake and traction control systems in hydraulic systems
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T15/00—Construction arrangement, or operation of valves incorporated in power brake systems and not covered by groups B60T11/00 or B60T13/00
    • B60T15/02—Application and release valves
    • B60T15/025—Electrically controlled valves
    • B60T15/028—Electrically controlled valves in hydraulic systems
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/50—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition having means for controlling the rate at which pressure is reapplied to or released from the brake
    • B60T8/5018—Pressure reapplication using restrictions
    • B60T8/5025—Pressure reapplication using restrictions in hydraulic brake systems

Definitions

  • the invention relates to an electromagnetically actuated valve, in particular for anti-lock braking systems in motor vehicles a valve housing which has an inlet and an outlet, - Two valve parts, one of which has a closing body and the other a valve seat, and - An electromagnet and a return spring with which one of the two valve parts can be moved back and forth with respect to the other between an open position and a closed position.
  • valve part In a known valve of this type (DE 3802648 A1), one of the valve parts with the closing body is pressed firmly into the valve housing and provided with a rod-shaped extension; on this the other, sleeve-shaped, valve part is slidably guided, on which the valve seat is formed.
  • the sleeve-shaped valve part forms the armature of the electromagnet and is biased by a return spring either in the opening direction or in the closing direction, depending on whether the valve is intended for the function "normally open” or "normally closed”.
  • the rod-shaped extension of the closing body he extends through the sleeve-shaped valve part and has practically the same diameter as the valve seat; consequently, no hydraulic forces need to be overcome when operating the valve. This means that short switching times in the range of milliseconds can be maintained with this known valve.
  • the valve part, on which the valve body is formed has an axial bore which, when the valve is open, determines the flow cross section.
  • the invention is therefore based on the object of designing an electromagnetically actuated valve, in particular for anti-lock braking systems in motor vehicles, such that when the valve is opened during a period in which there is still a pressure difference between the inlet and the outlet, one in comparison to the fully open one State any predetermined throttling takes place.
  • the object is achieved in a valve of the type described above in that an actuator is arranged in the valve housing, which is movable depending on a pressure difference between the inlet and outlet from a rest position to a stop position in which the control valve prevents the valve from fully opening .
  • a valve of the type described in the introduction has been closed, for example in an ABS control process, a considerable pressure drop between the inlet and the outlet can arise in a very short time.
  • This pressure drop which can cause an undesirably rapid rise in pressure at the outlet and in downstream units when subsequently opening known generic valves, is used in the valve according to the invention to bring the actuator into a predetermined stop position, in which it prevents the valve from opening fully for as long until the pressure difference between inlet and outlet has been reduced to a predetermined residual amount or even completely.
  • the actuator prevents the valve from opening completely, the flow of the fluid controlled by the valve between the closing body and the valve seat is throttled to a degree which depends on how the stop position of the actuator has been predetermined.
  • the stop position can be predetermined once and for all, for example by dimensioning the actuator and certain parts of the valve housing; in principle, however, there is also the possibility that the stop position is fixed by a screw or the like and consequently can be changed if necessary.
  • the actuator according to the invention can, for example, be movable in the manner of a bolt transversely to the stroke of the electromagnetically actuatable valve part in order to interrupt its opening movement at a specific point and thereby ensure a throttled flow through the valve until the pressure difference between its inlet and outlet in the desired Dimension has been reduced.
  • the actuator can also be arranged axially parallel to the valve part, the stroke of which it is intended to influence.
  • the actuator is preferably arranged coaxially with the two valve parts. This facilitates the machining of the valve housing, especially on a lathe.
  • the inlet is located at one end of the valve housing and the actuator defines a control chamber which is located at the other end of the valve housing.
  • valve parts with the closing body is fixedly arranged in the valve housing and has a rod-shaped extension, - The other, sleeve-shaped, valve part is slidably guided on the extension, on which the valve seat is formed, and - The inlet is connected to the control chamber by an axial channel which extends through the closing body together with its extension and through the actuator.
  • the first and the second are known from DE 3802648 A1 mentioned at the beginning.
  • both valve parts are movable with respect to the valve housing and one of them is controlled electromagnetically, while the second valve part is controlled by the actuator.
  • This embodiment is expediently developed such that the second valve part forms a unit with the actuator.
  • the actuator can be biased towards its rest position by a spring supported in the valve housing.
  • the actuator can also be ensured in another way that the actuator assumes its rest position when the pressure between the inlet and outlet of the valve according to the invention is equalized.
  • the actuator can be a differential or step piston or a membrane.
  • the invention is applicable to normally closed valves in the same way as to normally open valves.
  • 1 to 5 each show a valve according to the invention which is open in the idle state in an axial section.
  • Each of the valves 10 shown in FIGS. 1 to 5 has a valve housing 12 with an inlet 14 and an outlet 16.
  • the valve according to FIG. 1 has an additional connection 18 which, like the inlet 14, does not connect to one via a line 20 Master cylinder shown can be connected.
  • the outlet 16 can be connected via a line 22 to a wheel brake cylinder, also not shown.
  • Corresponding connections of the inlet 14 and the outlet 16 are also provided in the valves shown in FIGS. 2 to 5, without being shown again there.
  • Each of the five valves has a valve chamber 24 enclosed by the valve housing 12, in each of which at least approximately the same pressure prevails as at the outlet 16.
  • the valve housing 12 of each of the valves shown has a base-like lower section which is surrounded by two sealing rings 26 and 28 and can be inserted into a housing, not shown, of a conventional brake pressure modulator.
  • Each of the valves 10 shown has an electromagnet 30 with a coil 32, which is arranged in or around the valve housing 12, and with an armature 34, which is movably guided within the valve housing 12 along the main axis A thereof.
  • the armature 34 is used to actuate a valve part 36 which has a conical closing body 38 and which interacts with a valve part 40 which has an annular valve seat 42.
  • the armature 34 actuates the valve part 40, which in this case is sleeve-shaped, with the annular valve seat 42, while the valve part 36 with the closing body 38 is stationary with respect to the valve housing 12.
  • All valves 10 shown are open when de-energized; this is ensured by a return spring 44 which prestresses the armature 34 in the opening direction, upwards in all five drawings.
  • the return spring 44 is supported either on FIGS. 4 and 5 directly on the valve housing 12 or on FIGS. 1 to 3 on a perforated disk 46 which is fastened in the valve housing 12. 1 and 2, the disk 46 also forms a guide for the valve part 36 which can be actuated by the armature 34.
  • a cylindrical control chamber 48 is formed in the valve housing 12 coaxially with the valve parts 36 and 40, in which the pressure prevails regardless of the position of the valve parts 36 and 40 in relation to one another as at the inlet 14.
  • the control chamber 48 1 and 3 to 5 downwards, according to FIG. 2 upwards, limited by an actuator 50. 1 to 4, the actuator 50 is a piston which is normally urged into a rest position by a spring 52, in which the control chamber 48 has its smallest possible volume. 5, the actuator 50 is a membrane that automatically strives to take its rest position. The rest position of the actuator 50 is determined in any case by the design of the valve housing 12.
  • the actuator 50 can be pressed into a stop position by fluid pressure, if this is noticeably greater at the inlet 14 than at the outlet 16, downwards in FIGS. 1 and 3 to 5, but upwards in FIG. 2.
  • the stop position is also fixed once and for all, namely by a shoulder 54 formed in the valve housing 12.
  • the actuator 50 prevents the valve 10 from completely opening. According to FIG. 1, this is done in that a piston rod 56 formed on the actuator 50 reduces the normal opening stroke B of the closing body 38 by the distance C in the stop position of the actuator 50 which the actuator 50 is movable between its rest position and its stop position. As a result, the valve can only partially open, so that the fluid flow between the closing body 38 and the valve seat 42 is throttled to the desired extent.
  • the actuator 50 forms a unit with the valve part 40, which is independent of the electromagnet and on which, in this example, the valve seat 42 is formed. If the actuator 50 assumes its stop position, which in this case is the upper end position of the actuator 50, then the closing body 38 and the valve seat 42 are offset together in the closed state of the valve by the distance C from the rest position of the actuator 50. As a result, the partial amount C of the entire opening stroke B of the closing body 38 is already consumed at the beginning of the opening, so that the closing body 38 can only move away from the valve seat 42 by the amount B minus C as long as the actuator 50 assumes its stop position.
  • FIG. 1 shows some known details of an anti-lock braking system for motor vehicles, namely a line 58 which connects the lines 20 and 22 to one another and contains a shut-off valve 60, a pressure accumulator 62 and a pump 64.
  • the shut-off valve 60 like the valve 10, can be actuated electromagnetically, but, in contrast to this, is normally closed.
  • the shut-off valve 60 is opened in the usual manner when or immediately after the valve 10 is closed, so that brake fluid from the brake connected to the line 22 is temporarily absorbed by the pressure accumulator 62 and then by the pump 64 in line 20, and thus in the master brake cylinder, is returned.
  • anti-lock braking systems of which the valves shown in FIGS. 2 to 5 are provided.
  • the valve of FIG. 2 has the special feature that the actuator 50 is designed as a differential or step piston and is guided and sealed in a correspondingly stepped bore in the valve housing 12. The area between the piston seals is connected to the atmosphere by a relief channel 66. 2, a check valve 68 is arranged in the valve housing 12, which enables pressure equalization by backflow of fluid from the outlet 16 into a line (not shown) connected to the inlet 14.
  • the closing body 38 which is fixed to the housing in this example, has a rod-shaped, cylindrical extension 70, on which the sleeve-shaped valve part 40 controlled by the armature 34 is guided with the annular valve seat 42.
  • the upper end of the extension 70 forms the shoulder 54, which determines the stop position of the actuator 50 and thus the distance C by which the actuator 50 can be displaced from its rest position into its stop position, so that the normal opening stroke B of the valve part 40 by the distance C. is reduced.
  • the extension 70 of the closing body 38 in FIG. 3 has an axially continuous bore 72, which is adjoined by an axial through bore 74 in the actuator 50 opening into the control chamber 48, as a result of which the control chamber 48 is continuously, and at least approximately without throttling, with the inlet 14 connected is.
  • the closing body 38 is arranged fixed to the housing in that the associated valve part 36 is firmly pressed into a closure part 76 of the valve housing 12.
  • the distance C by which the actuator 50 can be moved results from the determination of the press-in depth of the valve part 36.
  • the additional connection 18 is arranged directly next to the inlet 14, in contrast to FIG. 1, where the additional connection 18 is arranged at the end of the valve housing 12 facing away from the inlet 14.
  • the actuator 50 is arranged axially between the closing body 38 and the control chamber 48.
  • actuator 50 has a through axial bore 74; 4, a piston-like central section 78 of the valve part 36 is guided in this.
  • the diameter of the bore 74 is smaller than the effective diameter of the valve seat 42.
  • valve 10 is therefore independent of the action of the spring 52 endeavors to open when there is a sufficient pressure at the inlet 14, friction and depending on the arrangement of the Valve also to overcome resistances due to gravity against displacement of the valve part 36 and the armature 34. 4 therefore remains functional even if the spring 52 should be broken.
  • the valve shown in FIG. 5 has, in addition to the already mentioned feature that the actuator 50 is a membrane, the further special feature that, in contrast to FIG. 3, the axially continuous bore 72 extends through the valve part 36 which is connected to the actuator 50 is connected to a common axial movement.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Transportation (AREA)
  • Electromagnetism (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Magnetically Actuated Valves (AREA)
  • Regulating Braking Force (AREA)

Abstract

In the valve casing (12) an actuator (50) is arranged, which can be moved from a rest position into a stop position as a function of a pressure differential between the inlet (14) and outlet (16) of the valve (10), in which latter position the actuator (50) prevents complete opening of the valve. This ensures that if the valve (10) opens during a period in which a pressure differential still exists between inlet (14) and outlet (16), any throttling arbitrarily predeterminable in relation to the completely opened state occurs. <IMAGE>

Description

Die Erfindung betrifft ein elektromagnetisch betätigtes Ventil, insbes. für Antiblockiersysteme in Kraftfahr­zeugen, mit
- einem Ventilgehäuse, das einen Einlaß und einen Auslaß aufweist,
- zwei Ventilteilen, von denen eines einen Schließkörper und das andere einen Ventilsitz aufweist, sowie
- einem Elektromagneten und einer Rückstellfeder, mit denen eines der beiden Ventilteile in bezug auf das andere zwischen einer Offenstellung und einer Schließstellung hin- und herbewegbar ist.The invention relates to an electromagnetically actuated valve, in particular for anti-lock braking systems in motor vehicles
a valve housing which has an inlet and an outlet,
- Two valve parts, one of which has a closing body and the other a valve seat, and
- An electromagnet and a return spring with which one of the two valve parts can be moved back and forth with respect to the other between an open position and a closed position.

Bei einem bekannten Ventil dieser Gattung (DE 3802648 A1) ist eines der Ventilteile mit dem Schließkörper in das Ventilgehäuse fest eingepreßt und mit einem stangenför­migen Fortsatz versehen; auf diesem ist das andere, hül­senförmige, Ventilteil verschiebbar geführt, an dem der Ventilsitz ausgebildet ist. Das hülsenförmige Ventilteil bildet den Anker des Elektromagneten und ist durch eine Rückstellfeder entweder in Öffnungsrichtung oder in Schließrichtung vorgespannt, je nachdem, ob das Ventil für die Funktion "stromlos auf" oder "stromlos zu" vorgesehen ist. Der stangenförmige Fortsatz des Schließkörpers er­ streckt sich durch das hülsenförmige Ventilteil hindurch und hat praktisch denselben Durchmesser wie der Ventil­sitz; infolgedessen brauchen beim Betätigen des Ventils keine hydraulischen Kräfte überwunden zu werden. Deshalb lassen sich mit diesem bekannten Ventil kurze Schaltzeiten im Bereich von Millisekunden einhalten. Das Ventilteil, an dem der Ventilkörper ausgebildet ist, weist eine axiale Bohrung auf, die bei geöffnetem Ventil den Durchflußquer­schnitt bestimmt.In a known valve of this type (DE 3802648 A1), one of the valve parts with the closing body is pressed firmly into the valve housing and provided with a rod-shaped extension; on this the other, sleeve-shaped, valve part is slidably guided, on which the valve seat is formed. The sleeve-shaped valve part forms the armature of the electromagnet and is biased by a return spring either in the opening direction or in the closing direction, depending on whether the valve is intended for the function "normally open" or "normally closed". The rod-shaped extension of the closing body he extends through the sleeve-shaped valve part and has practically the same diameter as the valve seat; consequently, no hydraulic forces need to be overcome when operating the valve. This means that short switching times in the range of milliseconds can be maintained with this known valve. The valve part, on which the valve body is formed, has an axial bore which, when the valve is open, determines the flow cross section.

Bei der Bemessung des Durchflußquerschnittes gattungs­gemäßer Ventile muß ein Kompromiß zwischen widersprüch­lichen Anforderungen gefunden werden. Im allgemeinen ist es wünschenswert, daß der Durchflußquerschnitt möglichst groß ist. Dies gilt besonders bei Verwendung solcher Ven­tile in Antiblockiersystemen für Kraftfahrzeuge; dort läßt sich eine bei normaler Bremsbetätigung angestrebte kurze Ansprechzeit der Bremsen nur dann einhalten, wenn die Strömung der Bremsflüssigkeit vom Hauptbremszylinder zu den Radbremszylindern nirgends erheblich gedrosselt wird. Andererseits ist eine gewisse Drosselung der Strömung im Ventil erwünscht, wenn dieses geöffnet wird, nachdem es wegen Blockiergefahr eines ihm zugeordneten Rades ge­schlossen worden ist. In diesem Fall könnte ein ungedros­selter Druckaufbau im Ventil dazu beitragen, eine erneute Blockiergefahr hervorzurufen. Damit in diesem Betriebs­zustand eine ausreichende Drosselung erreicht wird, ist es üblich, bekannte Ventile der eingangs genannten Gattung mit einer verhältnismäßig engen, fest eingebauten Drossel­stelle auszustatten. Dabei wird ein etwas verzögertes An­sprechen der Bremsen bei normaler Betätigung in Kauf ge­nommen.When designing the flow cross-section of generic valves, a compromise must be found between contradicting requirements. In general, it is desirable that the flow area be as large as possible. This applies particularly when using such valves in anti-lock braking systems for motor vehicles; there a short response time of the brakes aimed at during normal brake actuation can only be maintained if the flow of the brake fluid from the master brake cylinder to the wheel brake cylinders is nowhere significantly restricted. On the other hand, a certain throttling of the flow in the valve is desirable when it is opened after it has been closed due to the risk of a wheel associated with it blocking. In this case, an unthrottled pressure build-up in the valve could help to create a new risk of locking. So that sufficient throttling is achieved in this operating state, it is customary to equip known valves of the type mentioned at the outset with a relatively narrow, fixed throttling point. A somewhat delayed brake response during normal operation is accepted.

Es ist allerdings auch bekannt (DE 3725810 A1), bei einem Magnetventil für ein Antiblockiersystem einen Einström­ bereich, ein Dichtelement in Form einer Dichtkugel und einen Dichtelementträger in Form einer Lochscheibe so auszubilden, daß sich innerhalb bestimmter Hub- und Durchflußbereiche ein Ansaugeffekt durch die strömende Bremsflüssigkeit ergibt. Dabei ist ein auf den Anker des Elektromagneten wirkendes Rückhalteelement in Form eines Permanentmagneten oder einer Schnappfeder so angeordnet, daß es bei elektrischer Ansteuerung des Magnetventils durch die Ankerbewegung überwunden wird. Dadurch soll sich ein großer Durchflußquerschnitt für Normalbremsung und ein reduzierter Durchflußquerschnitt bei ABS-Betrieb ergeben. Der Ansaugeffekt, der auf dem sogenannten hydrodynamischen Paradoxon beruht, tritt jedoch nur in einem eng begrenzten Hubbereich auf. Es ist daher kaum möglich, das Ventil so auszulegen, daß für Normalfälle, insbes. normale Bremsun­gen, einerseits und für Regelung, insbes. für ABS-Betrieb, andererseits optimale und stabile Strömungsverhältnisse erreicht werden.However, it is also known (DE 3725810 A1) that an inflow occurs in a magnetic valve for an anti-lock braking system area to form a sealing element in the form of a sealing ball and a sealing element carrier in the form of a perforated disc so that there is a suction effect by the flowing brake fluid within certain stroke and flow ranges. A retaining element acting on the armature of the electromagnet in the form of a permanent magnet or a snap spring is arranged in such a way that it is overcome by the armature movement when the solenoid valve is electrically actuated. This should result in a large flow cross section for normal braking and a reduced flow cross section in ABS operation. The suction effect, which is based on the so-called hydrodynamic paradox, only occurs in a narrowly limited stroke range. It is therefore hardly possible to design the valve in such a way that optimal and stable flow conditions are achieved for normal cases, in particular normal braking, on the one hand and for control, in particular for ABS operation.

Der Erfindung liegt deshalb die Aufgabe zugrunde, ein elektromagnetisch betätigtes Ventil, insbes. für Anti­blockiersysteme in Kraftfahrzeugen, derart zu gestalten, daß beim Öffnen des Ventils während einer Zeitspanne, in der ein Druckunterschied zwischen Einlaß und Auslaß noch besteht, eine im Vergleich zum vollständig geöffneten Zustand beliebig vorbestimmbare Drosselung stattfindet.The invention is therefore based on the object of designing an electromagnetically actuated valve, in particular for anti-lock braking systems in motor vehicles, such that when the valve is opened during a period in which there is still a pressure difference between the inlet and the outlet, one in comparison to the fully open one State any predetermined throttling takes place.

Die Aufgabe ist erfindungsgemäß bei einem Ventil der ein­gangs beschriebenen Gattung dadurch gelöst, daß im Ventil­gehäuse ein Stellglied angeordnet ist, das abhängig von einem Druckunterschied zwischen Einlaß und Auslaß aus einer Ruhestellung in eine Anschlagstellung bewegbar ist, in der das Stellgleid ein vollständiges Öffnen des Ventils verhindert.The object is achieved in a valve of the type described above in that an actuator is arranged in the valve housing, which is movable depending on a pressure difference between the inlet and outlet from a rest position to a stop position in which the control valve prevents the valve from fully opening .

Wenn ein Ventil der eingangs beschriebenen Gattung geschlossen worden ist, beispielsweise bei einem ABS-­Regelvorgang, kann in sehr kurzer Zeit ein erhebliches Druckgefälle zwischen dem Einlaß und dem Auslaß entstehen. Dieses Druckgefälle, das beim anschließenden Öffnen be­kannter gattungsgemäßer Ventile einen unerwünscht raschen Druckanstieg am Auslaß und in nachgeordneten Aggregaten hervorrufen kann, wird bei dem erfindungsgemäßen Ventil genutzt, um das Stellglied in eine vorbestimmte Anschlag­stellung zu bringen, in der es ein vollständiges Öffnen des Ventils solange verhindert, bis der Druckunterschied zwischen Einlaß und Auslaß auf einen vorbestimmten Rest­betrag oder sogar vollständig abgebaut worden ist. Solange das Stellglied ein vollständiges Öffnen des Ventils ver­hindert, wird die Strömung des vom Ventil gesteuerten Fluids zwischen dem Schließkörper und dem Ventilsitz in einem Maß gedrosselt, das davon abhängt, wie die Anschlag­stellung des Stellgliedes vorbestimmt worden ist. Die Anschlagstellung kann ein für allemal, beispielsweise durch Bemessung des Stellgliedes und bestimmter Teile des Ventilgehäuses, vorbestimmt sein; grundsätzlich besteht aber auch die Möglichkeit, daß die Anschlagstellung durch eine Schraube oder dergleichen festgelegt und infolgedes­sen bei Bedarf veränderbar ist.If a valve of the type described in the introduction has been closed, for example in an ABS control process, a considerable pressure drop between the inlet and the outlet can arise in a very short time. This pressure drop, which can cause an undesirably rapid rise in pressure at the outlet and in downstream units when subsequently opening known generic valves, is used in the valve according to the invention to bring the actuator into a predetermined stop position, in which it prevents the valve from opening fully for as long until the pressure difference between inlet and outlet has been reduced to a predetermined residual amount or even completely. As long as the actuator prevents the valve from opening completely, the flow of the fluid controlled by the valve between the closing body and the valve seat is throttled to a degree which depends on how the stop position of the actuator has been predetermined. The stop position can be predetermined once and for all, for example by dimensioning the actuator and certain parts of the valve housing; in principle, however, there is also the possibility that the stop position is fixed by a screw or the like and consequently can be changed if necessary.

Das erfindungsgemäße Stellglied kann beispielsweise in der Art eines Riegels quer zur Hubstrecke des elektromagne­tisch betätigbaren Ventilteils bewegbar sein, um dessen Öffnungsbewegung an einer bestimmten Stelle zu unterbre­chen und dadurch für eine gedrosselte Durchströmung des Ventils zu sorgen, bis der Druckunterschied zwischen dessen Einlaß und Auslaß im gewünschten Maß abgebaut worden ist. Das Stellglied kann auch achsparallel zu dem Ventilteil angeordnet sein, dessen Hub er beeinflussen soll.The actuator according to the invention can, for example, be movable in the manner of a bolt transversely to the stroke of the electromagnetically actuatable valve part in order to interrupt its opening movement at a specific point and thereby ensure a throttled flow through the valve until the pressure difference between its inlet and outlet in the desired Dimension has been reduced. The actuator can also be arranged axially parallel to the valve part, the stroke of which it is intended to influence.

Vorzugsweise ist das Stellglied jedoch gleichachsig mit den beiden Ventilteilen angeordnet. Dadurch wird die Bear­beitung des Ventilgehäuses, insbes. auf einer Drehmaschi­ne, erleichtert.However, the actuator is preferably arranged coaxially with the two valve parts. This facilitates the machining of the valve housing, especially on a lathe.

Bei einer Ausführungsform der Erfindung ist der Einlaß, wie üblich, an einem Ende des Ventilgehäuses angeordnet, und das Stellglied begrenzt eine Steuerkammer, die am anderen Ende des Ventilgehäuses angeordnet ist.In one embodiment of the invention, as usual, the inlet is located at one end of the valve housing and the actuator defines a control chamber which is located at the other end of the valve housing.

Diese Ausführungsform kann dadurch weitergebildet sein, daß
- eines der Ventilteile mit dem Schließkörper im Ventil­gehäuse fest angeordnet ist und einen stangenförmigen Fortsatz aufweist,
- auf dem Fortsatz das andere, hülsenförmige, Ventilteil verschiebbar geführt ist, an dem der Ventilsitz ausgebil­det ist, und
- der Einlaß mit der Steuerkammer durch einen axialen Kanal verbunden ist, der sich durch den Schließkörper samt seinem Fortsatz und durch das Stellglied hindurch­erstreckt.This embodiment can be further developed in that
one of the valve parts with the closing body is fixedly arranged in the valve housing and has a rod-shaped extension,
- The other, sleeve-shaped, valve part is slidably guided on the extension, on which the valve seat is formed, and
- The inlet is connected to the control chamber by an axial channel which extends through the closing body together with its extension and through the actuator.

Von den vorstehend beschriebenen drei weiterbildenden Merkmalen sind das erste und das zweite aus der eingangs erwähnten DE 3802648 A1 bekannt.Of the three further features described above, the first and the second are known from DE 3802648 A1 mentioned at the beginning.

Bei einer anderen Ausführungsform der Erfindung sind beide Ventilteile in bezug auf das Ventilgehäuse beweglich, und eines von ihnen ist elektromagnetisch gesteuert, während das zweite Ventilteil vom Stellglied gesteuert ist. Diese Ausführungsform ist zweckmäßigerweise derart weitergebil­det, daß das zweite Ventilteil mit dem Stellglied eine Einheit bildet.In another embodiment of the invention, both valve parts are movable with respect to the valve housing and one of them is controlled electromagnetically, while the second valve part is controlled by the actuator. This embodiment is expediently developed such that the second valve part forms a unit with the actuator.

Bei allen beschriebenen Ausführungsformen kann das Stell­glied in Richtung zu seiner Ruhestellung hin von einer im Ventilgehäuse abgestützten Feder vorgespannt sein. Es kann aber auch auf andere Weise dafür gesorgt sein, daß das Stellglied bei Druckausgleich zwischen Einlaß und Auslaß des erfindungsgemäßen Ventils seine Ruhestellung einnimmt. Beispielsweise kann das Stellglied ein Differential- oder Stufenkolben oder eine Membran sein.In all the described embodiments, the actuator can be biased towards its rest position by a spring supported in the valve housing. However, it can also be ensured in another way that the actuator assumes its rest position when the pressure between the inlet and outlet of the valve according to the invention is equalized. For example, the actuator can be a differential or step piston or a membrane.

Die Erfindung ist auf normalerweise geschlossene Ventile in gleicher Weise anwendbar wie auf normalerweise offene Ventile.The invention is applicable to normally closed valves in the same way as to normally open valves.

Ausführungsbeispiele der Erfindung werden im folgenden anhand schematischer Zeichnungen mit weiteren Einzelheiten beschrieben. In Fig. 1 bis 5 ist je ein erfindungsgemäßes, im Ruhezustand offenes Ventil in einem axialen Schnitt dargestellt.Exemplary embodiments of the invention are described below with the aid of schematic drawings with further details. 1 to 5 each show a valve according to the invention which is open in the idle state in an axial section.

Jedes der in Fig. 1 bis 5 dargestellten Ventile 10 hat ein Ventilgehäuse 12 mit einem Einlaß 14 und einem Auslaß 16. Das Ventil gemäß Fig. 1 hat einen zusätzlichen Anschluß 18, der sich ebenso wie der Einlaß 14 über eine Leitung 20 an einen nicht dargestellten Hauptbremszylinder an­schließen läßt. Der Auslaß 16 läßt sich über eine Leitung 22 an einen ebenfalls nicht dargestellten Radbremszylinder anschließen. Entsprechende Anschlüsse des Einlasses 14 und des Auslasses 16 sind auch bei den in Fig. 2 bis 5 darge­stellten Ventilen vorgesehen, ohne dort noch einmal dar­gestellt zu sein.Each of the valves 10 shown in FIGS. 1 to 5 has a valve housing 12 with an inlet 14 and an outlet 16. The valve according to FIG. 1 has an additional connection 18 which, like the inlet 14, does not connect to one via a line 20 Master cylinder shown can be connected. The outlet 16 can be connected via a line 22 to a wheel brake cylinder, also not shown. Corresponding connections of the inlet 14 and the outlet 16 are also provided in the valves shown in FIGS. 2 to 5, without being shown again there.

Jedes der fünf Ventile weist eine vom Ventilgehäuse 12 umschlossene Ventilkammer 24 auf, in der jeweils minde­stens annähernd der gleiche Druck herrscht wie am Auslaß 16. Das Ventilgehäuse 12 jedes der dargestellten Ventile hat einen sockelartigen unteren Abschnitt, der von zwei Dichtringen 26 und 28 umschlossen ist und sich in ein nicht dargestelltes Gehäuse eines üblichen Bremsdruck­modulators einstecken läßt.Each of the five valves has a valve chamber 24 enclosed by the valve housing 12, in each of which at least approximately the same pressure prevails as at the outlet 16. The valve housing 12 of each of the valves shown has a base-like lower section which is surrounded by two sealing rings 26 and 28 and can be inserted into a housing, not shown, of a conventional brake pressure modulator.

Jedes der dargestellten Ventile 10 hat einen Elektromagne­ten 30 mit einer Spule 32, die im Ventilgehäuse 12 oder rings um dieses angeordnet ist, und mit einem Anker 34, der innerhalb des Ventilgehäuses 12 längs dessen Haupt­achse A beweglich geführt ist. Der Anker 34 dient bei den Ventilen gemäß Fig. 1, 2, 4 und 5 zum Betätigen eines Ven­tilteils 36, das einen kegelförmigen Schließkörper 38 auf­weist und mit einem Ventilteil 40 zusammenwirkt, das einen ringförmigen Ventilsitz 42 aufweist. Bei der Ausführungs­form gemäß Fig. 3 betätigt der Anker 34 hingegen das in diesem Fall hülsenförmig gestaltete Ventilteil 40 mit dem ringförmigen Ventilsitz 42, während das Ventilteil 36 mit dem Schließkörper 38 in bezug auf das Ventilgehäuse 12 ortsfest ist.Each of the valves 10 shown has an electromagnet 30 with a coil 32, which is arranged in or around the valve housing 12, and with an armature 34, which is movably guided within the valve housing 12 along the main axis A thereof. In the valves according to FIGS. 1, 2, 4 and 5, the armature 34 is used to actuate a valve part 36 which has a conical closing body 38 and which interacts with a valve part 40 which has an annular valve seat 42. In the embodiment according to FIG. 3, on the other hand, the armature 34 actuates the valve part 40, which in this case is sleeve-shaped, with the annular valve seat 42, while the valve part 36 with the closing body 38 is stationary with respect to the valve housing 12.

Alle dargestellten Ventile 10 sind in stromlosem Zustand offen; dafür sorgt eine Rückstellfeder 44, die den Anker 34 in Öffnungsrichtung, in allen fünf Zeichnungen nach oben, vorspannt. Die Rückstellfeder 44 stützt sich ent­weder gemäß Fig. 4 und 5 unmittelbar am Ventilgehäuse 12 ab oder gemäß Fig. 1 bis 3 an einer gelochten Scheibe 46, die im Ventilgehäuse 12 befestigt ist. Gemäß Fig. 1 und 2 bildet die Scheibe 46 zugleich eine Führung für das vom Anker 34 betätigbare Ventilteil 36.All valves 10 shown are open when de-energized; this is ensured by a return spring 44 which prestresses the armature 34 in the opening direction, upwards in all five drawings. The return spring 44 is supported either on FIGS. 4 and 5 directly on the valve housing 12 or on FIGS. 1 to 3 on a perforated disk 46 which is fastened in the valve housing 12. 1 and 2, the disk 46 also forms a guide for the valve part 36 which can be actuated by the armature 34.

Gemäß Fig. 1 bis 5 ist im Ventilgehäuse 12 gleichachsig mit den Ventilteilen 36 und 40 eine zylindrische Steuer­kammer 48 ausgebildet, in der unabhängig von der Stellung der Ventilteile 36 und 40 in bezug zueinander der gleiche Druck herrscht wie am Einlaß 14. Die Steuerkammer 48 ist gemäß Fig. 1 und 3 bis 5 nach unten, gemäß Fig. 2 hingegen nach oben, durch ein Stellglied 50 begrenzt. Gemäß Fig. 1 bis 4 ist das Stellglied 50 ein Kolben, der durch eine Feder 52 normalerweise in eine Ruhestellung gedrängt wird, in der die Steuerkammer 48 ihr kleinstmögliches Volumen hat. Gemäß Fig. 5 ist das Stellglied 50 eine Membran, die von selbst bestrebt ist, ihre Ruhestellung einzunehmen. Die Ruhestellung des Stellgliedes 50 ist in jedem Fall durch die Gestaltung des Ventilgehäuses 12 genau fest­gelegt.1 to 5, a cylindrical control chamber 48 is formed in the valve housing 12 coaxially with the valve parts 36 and 40, in which the pressure prevails regardless of the position of the valve parts 36 and 40 in relation to one another as at the inlet 14. The control chamber 48 1 and 3 to 5 downwards, according to FIG. 2 upwards, limited by an actuator 50. 1 to 4, the actuator 50 is a piston which is normally urged into a rest position by a spring 52, in which the control chamber 48 has its smallest possible volume. 5, the actuator 50 is a membrane that automatically strives to take its rest position. The rest position of the actuator 50 is determined in any case by the design of the valve housing 12.

Aus der Ruhestellung läßt sich das Stellglied 50 durch Fluiddruck, wenn dieser am Einlaß 14 merklich größer als am Auslaß 16 ist, in eine Anschlagstellung drängen, in Fig. 1 und 3 bis 5 nach unten, in Fig. 2 hingegen nach oben. In allen Ausführungsbeispielen ist auch die An­schlagstellung ein für allemal festgelegt, nämlich durch eine im Ventilgehäuse 12 ausgebildete Schulter 54.From the rest position, the actuator 50 can be pressed into a stop position by fluid pressure, if this is noticeably greater at the inlet 14 than at the outlet 16, downwards in FIGS. 1 and 3 to 5, but upwards in FIG. 2. In all exemplary embodiments, the stop position is also fixed once and for all, namely by a shoulder 54 formed in the valve housing 12.

In seiner Anschlagstellung verhindert das Stellglied 50 ein vollständiges Öffnen des Ventils 10. Gemäß Fig. 1 ge­schieht dies dadurch, daß eine am Stellglied 50 ausgebil­dete Kolbenstange 56 in der Anschlagstellung des Stell­gliedes 50 den normalen Öffnungshub B des Schließkörpers 38 um die Strecke C vermindert, um die das Stellglied 50 zwischen seiner Ruhestellung und seiner Anschlagstellung bewegbar ist. Das Ventil kann sich infolgedessen nur teilweise öffnen, so daß die Fluidströmung zwischen Schließkörper 38 und Ventilsitz 42 in dem gewünschten Maß gedrosselt wird.In its stop position, the actuator 50 prevents the valve 10 from completely opening. According to FIG. 1, this is done in that a piston rod 56 formed on the actuator 50 reduces the normal opening stroke B of the closing body 38 by the distance C in the stop position of the actuator 50 which the actuator 50 is movable between its rest position and its stop position. As a result, the valve can only partially open, so that the fluid flow between the closing body 38 and the valve seat 42 is throttled to the desired extent.

In entsprechender Weise wird gemäß Fig. 3 bis 5 der normale Öffnungshub B des Ventilsitzes 42 um die Strecke C vermindert und somit nur eine gedrosselte Fluidströmung zugelassen, wenn das Stellglied 50 seine Anschlagstellung einnimmt.3 to 5, the normal opening stroke B of the valve seat 42 is reduced by the distance C and thus only a throttled fluid flow is permitted when the actuator 50 assumes its stop position.

Eine andere Art, ein vollständiges Öffnen des Ventils zu verhindern und somit eine Drosselung zu bewirken, ergibt sich aus der Gestaltung gemäß Fig. 2. Dort bildet das Stellglied 50 eine Einheit mit dem vom Elektromagneten unabhängigen Ventilteil 40, an dem in diesem Beispiel der Ventilsitz 42 ausgebildet ist. Wenn das Stellglied 50 seine Anschlagstellung einnimmt, die in diesem Fall die obere Endstellung des Stellgliedes 50 ist, dann sind Schließkörper 38 und Ventilsitz 42 im geschlossenen Zu­stand des Ventils gemeinsam um die Strecke C gegenüber der Ruhestellung des Stellgliedes 50 nach oben versetzt. Da­durch ist von dem gesamten Öffnungshub B des Schließkör­pers 38 zu Beginn des Öffnens schon der Teilbetrag C ver­braucht, so daß der Schließkörper 38 sich nur noch um den Betrag B minus C vom Ventilsitz 42 entfernen kann, solange das Stellglied 50 seine Anschlagstellung einnimmt.Another way of preventing a complete opening of the valve and thus of throttling results from the design according to FIG. 2. There, the actuator 50 forms a unit with the valve part 40, which is independent of the electromagnet and on which, in this example, the valve seat 42 is formed. If the actuator 50 assumes its stop position, which in this case is the upper end position of the actuator 50, then the closing body 38 and the valve seat 42 are offset together in the closed state of the valve by the distance C from the rest position of the actuator 50. As a result, the partial amount C of the entire opening stroke B of the closing body 38 is already consumed at the beginning of the opening, so that the closing body 38 can only move away from the valve seat 42 by the amount B minus C as long as the actuator 50 assumes its stop position.

In Fig. 1 sind neben dem Ventil 10 einige bekannte Einzel­heiten eines Antiblockiersystems für Kraftfahrzeuge dar­gestellt, nämlich eine Leitung 58, welche die Leitungen 20 und 22 miteinander verbindet und ein Absperrventil 60, einen Druckspeicher 62 und eine Pumpe 64 enthält. Das Ab­sperrventil 60 ist ebenso wie das Ventil 10 elektromagne­tisch betätigbar, ist jedoch im Gegensatz zu diesem nor­malerweise geschlossen.In addition to the valve 10, FIG. 1 shows some known details of an anti-lock braking system for motor vehicles, namely a line 58 which connects the lines 20 and 22 to one another and contains a shut-off valve 60, a pressure accumulator 62 and a pump 64. The shut-off valve 60, like the valve 10, can be actuated electromagnetically, but, in contrast to this, is normally closed.

Bei Antiblockierregelung wird das Absperrventil 60 in üblicher Weise bei oder unmittelbar nach dem Schließen des Ventils 10 geöffnet, so daß Bremsflüssigkeit aus der an die Leitung 22 angeschlossenen Bremse vorübergehend vom Druckspeicher 62 aufgenommen und dann von der Pumpe 64 in die Leitung 20, und somit in den Hauptbremszylinder, zurückgefördert wird. Entsprechendes gilt auch für Anti­blockiersysteme, als deren Bestandteil die in Fig. 2 bis 5 dargestellten Ventile vorgesehen sind.With anti-lock control, the shut-off valve 60 is opened in the usual manner when or immediately after the valve 10 is closed, so that brake fluid from the brake connected to the line 22 is temporarily absorbed by the pressure accumulator 62 and then by the pump 64 in line 20, and thus in the master brake cylinder, is returned. The same also applies to anti-lock braking systems, of which the valves shown in FIGS. 2 to 5 are provided.

Das Ventil gemäß Fig. 2 hat noch die Besonderheit, daß das Stellglied 50 als Differential- oder Stufenkolben ausgebil­det und in einer entsprechend gestuften Bohrung des Ven­tilgehäuses 12 geführt und abgedichtet ist. Der zwischen den Kolbendichtungen liegende Bereich ist durch einen Ent­lastungskanal 66 mit der Atmosphäre verbunden. Parallel zum Stellglied 50 ist gemäß Fig. 2 im Ventilgehäuse 12 ein Rückschlagventil 68 angeordnet, das einen Druckausgleich durch Rückströmung von Fluid vom Auslaß 16 in eine nicht dargestellte, mit dem Einlaß 14 verbundene Leitung ermög­licht.The valve of FIG. 2 has the special feature that the actuator 50 is designed as a differential or step piston and is guided and sealed in a correspondingly stepped bore in the valve housing 12. The area between the piston seals is connected to the atmosphere by a relief channel 66. 2, a check valve 68 is arranged in the valve housing 12, which enables pressure equalization by backflow of fluid from the outlet 16 into a line (not shown) connected to the inlet 14.

Gemäß Fig. 3 hat der in diesem Beispiel gehäusefeste Schließkörper 38 einen stangenförmigen, zylindrischen Fortsatz 70, auf dem das hülsenförmig gestaltete, vom Anker 34 gesteuerte Ventilteil 40 mit dem ringförmigen Ventilsitz 42 geführt ist. Das obere Ende des Fortsatzes 70 bildet die Schulter 54, welche die Anschlagstellung des Stellgliedes 50 und somit die Strecke C bestimmt, um die das Stellglied 50 aus seiner Ruhestellung in seine An­schlagstellung verschiebbar ist, damit der normale Öff­nungshub B des Ventilteils 40 um die Strecke C vermindert wird.According to FIG. 3, the closing body 38, which is fixed to the housing in this example, has a rod-shaped, cylindrical extension 70, on which the sleeve-shaped valve part 40 controlled by the armature 34 is guided with the annular valve seat 42. The upper end of the extension 70 forms the shoulder 54, which determines the stop position of the actuator 50 and thus the distance C by which the actuator 50 can be displaced from its rest position into its stop position, so that the normal opening stroke B of the valve part 40 by the distance C. is reduced.

Der Fortsatz 70 des Schließkörpers 38 in Fig. 3 hat eine axial durchgehende Bohrung 72, an die sich eine in die Steuerkammer 48 mündende axiale Durchgangsbohrung 74 im Stellglied 50 anschließt, wodurch die Steuerkammer 48 ständig, und zumindest annähernd ohne Drosselung, mit dem Einlaß 14 verbunden ist. Der Schließkörper 38 ist gemäß Fig. 3 dadurch gehäusefest angeordnet, daß das zugehörige Ventilteil 36 in ein Verschlußteil 76 des Ventilgehäuses 12 fest eingepreßt ist. Aus der Festlegung der Einpreß­tiefe des Ventilteils 36 ergibt sich die Strecke C, um die das Stellglied 50 bewegbar ist.The extension 70 of the closing body 38 in FIG. 3 has an axially continuous bore 72, which is adjoined by an axial through bore 74 in the actuator 50 opening into the control chamber 48, as a result of which the control chamber 48 is continuously, and at least approximately without throttling, with the inlet 14 connected is. According to FIG. 3, the closing body 38 is arranged fixed to the housing in that the associated valve part 36 is firmly pressed into a closure part 76 of the valve housing 12. The distance C by which the actuator 50 can be moved results from the determination of the press-in depth of the valve part 36.

Gemäß Fig. 4 ist der zusätzliche Anschluß 18 unmittelbar neben dem Einlaß 14 angeordnet, im Gegensatz zu Fig. 1, wo der zusätzliche Anschluß 18 an dem vom Einlaß 14 abgewand­ten Ende des Ventilgehäuses 12 angeordnet ist. Eine wei­tere Besonderheit der in Fig. 4 dargestellten Ausführungs­form besteht darin, daß das Stellglied 50 axial zwischen dem Schließkörper 38 und der Steuerkammer 48 angeordnet ist. Wie in Fig. 3 hat das Stellglied 50 eine durchgehende axiale Bohrung 74; in dieser ist gemäß Fig. 4 ein kolben­artig gestalteter Mittelabschnitt 78 des Ventilteils 36 geführt. Der Durchmesser der Bohrung 74 ist kleiner als der wirksame Durchmesser des Ventilsitzes 42. Das Ventil 10 ist deshalb unabhängig von der Wirkung der Feder 52 be­strebt, sich zu öffnen, wenn am Einlaß 14 ein Druck anliegt, der ausreicht, Reibung und je nach Anordnung des Ventils auch durch Schwerkraft bedingte Widerstände gegen eine Verschiebung des Ventilteils 36 und des Ankers 34 zu überwinden. Das Ventil gemäß Fig. 4 bleibt deshalb auch dann funktionsfähig, wenn die Feder 52 gebrochen sein sollte.4, the additional connection 18 is arranged directly next to the inlet 14, in contrast to FIG. 1, where the additional connection 18 is arranged at the end of the valve housing 12 facing away from the inlet 14. Another special feature of the embodiment shown in FIG. 4 is that the actuator 50 is arranged axially between the closing body 38 and the control chamber 48. As in Figure 3, actuator 50 has a through axial bore 74; 4, a piston-like central section 78 of the valve part 36 is guided in this. The diameter of the bore 74 is smaller than the effective diameter of the valve seat 42. The valve 10 is therefore independent of the action of the spring 52 endeavors to open when there is a sufficient pressure at the inlet 14, friction and depending on the arrangement of the Valve also to overcome resistances due to gravity against displacement of the valve part 36 and the armature 34. 4 therefore remains functional even if the spring 52 should be broken.

Das in Fig. 5 dargestellte Ventil hat neben dem schon erwähnten Merkmal, daß das Stellglied 50 eine Membran ist, die weitere Besonderheit, daß die axial durchgehende Boh­rung 72 sich im Gegensatz zu Fig. 3 durch das Ventilteil 36 erstreckt, das mit dem Stellglied 50 zu gemeinsamer Axialbewegung verbunden ist.The valve shown in FIG. 5 has, in addition to the already mentioned feature that the actuator 50 is a membrane, the further special feature that, in contrast to FIG. 3, the axially continuous bore 72 extends through the valve part 36 which is connected to the actuator 50 is connected to a common axial movement.

Claims (12)

1. Elektromagnetisch betätigtes Ventil, insbes. für Antiblockiersysteme in Kraftfahrzeugen, mit
- einem Ventilgehäuse (12), das einen Einlaß (14) und einen Auslaß (16) aufweist,
- zwei Ventilteilen (36, 40), von denen eines einen Schließkörper (38) und das andere einen Ventilsitz (42) aufweist, sowie
- einem Elektromagneten (30) und einer Rückstellfeder (46), mit denen eines der beiden Ventilteile (36, 40) in bezug auf das andere zwischen einer Offenstellung und einer Schließstellung hin- und herbewegbar ist,
dadurch gekennzeichnet, daß im Ventil­gehäuse (12) ein Stellglied (50) angeordnet ist, das ab­hängig von einem Druckunterschied zwischen Einlaß (14) und Auslaß (16) aus einer Ruhestellung in eine Anschlagstel­lung bewegbar ist, in der das Stellglied (50) ein voll­ständiges Öffnen des Ventils verhindert.1. Electromagnetically operated valve, in particular for anti-lock braking systems in motor vehicles, with
- a valve housing (12) which has an inlet (14) and an outlet (16),
- Two valve parts (36, 40), one of which has a closing body (38) and the other a valve seat (42), and
an electromagnet (30) and a return spring (46) with which one of the two valve parts (36, 40) can be moved back and forth in relation to the other between an open position and a closed position,
characterized in that an actuator (50) is arranged in the valve housing (12) which, depending on a pressure difference between the inlet (14) and outlet (16), can be moved from a rest position into a stop position in which the actuator (50) is complete Opening of the valve prevented. 2. Ventil nach Anspruch 1,
dadurch gekennzeichnet, daß das Stell­glied (50) gleichachsig mit den beiden Ventilteilen (36, 40) angeordnet ist.2. Valve according to claim 1,
characterized in that the actuator (50) is arranged coaxially with the two valve parts (36, 40). 3. Ventil nach Anspruch 2,
dadurch gekennzeichnet, daß der Einlaß (14) an einem Ende des Ventilgehäuses (12) angeordnet ist und das Stellglied (50) eine Steuerkammer (48) begrenzt, die am anderen Ende des Ventilgehäuses (12) angeordnet ist.3. Valve according to claim 2,
characterized in that the inlet (14) is located at one end of the valve housing (12) and the actuator (50) defines a control chamber (48) which is located at the other end of the valve housing (12). 4. Ventil nach Anspruch 3,
dadurch gekennzeichnet, daß
- eines der Ventilteile (36) mit dem Schließkörper (38) im Ventilgehäuse (12) fest angeordnet ist und einen stangen­förmigen Fortsatz (70) aufweist,
- auf dem Fortsatz (70) das andere, hülsenförmige, Ventil­teil (40) verschiebbar geführt ist, an dem der Ventilsitz (42) ausgebildet ist, und
- der Einlaß (14) mit der Steuerkammer (48) durch einen axialen Kanal (72, 74) verbunden ist, der sich durch den Schließkörper (38) samt seinem Fortsatz (70) und durch das Stellglied (50) hindurcherstreckt.4. Valve according to claim 3,
characterized in that
one of the valve parts (36) with the closing body (38) is fixed in the valve housing (12) and has a rod-shaped extension (70),
- On the extension (70) the other, sleeve-shaped, valve part (40) is slidably guided, on which the valve seat (42) is formed, and
- The inlet (14) is connected to the control chamber (48) through an axial channel (72, 74) which extends through the closing body (38) together with its extension (70) and through the actuator (50). 5. Ventil nach Anspruch 2,
dadurch gekennzeichnet, daß beide Ventil­teile (36, 40) in bezug auf das Ventilgehäuse (12) beweg­lich sind, eines (36) von ihnen vom Elektromagneten (30), und das zweite Ventilteil (40) vom Stellglied (50) ge­steuert ist.5. Valve according to claim 2,
characterized in that both valve parts (36, 40) are movable with respect to the valve housing (12), one (36) of which is controlled by the electromagnet (30) and the second valve part (40) is controlled by the actuator (50). 6. Ventil nach Anspruch 5,
dadurch gekennzeichnet, daß das zweite Ventilteil (40) mit dem Stellglied (50) eine Einheit bildet.6. Valve according to claim 5,
characterized in that the second valve part (40) forms a unit with the actuator (50). 7. Ventil nach einem der Ansprüche 1 bis 6,
dadurch gekennzeichnet, daß das Stell­glied (50) in Richtung zu seiner Ruhestellung hin von einer im Ventilgehäuse (12) abgestützten Feder (52) vorgespannt ist.7. Valve according to one of claims 1 to 6,
characterized in that the actuator (50) is biased towards its rest position by a spring (52) supported in the valve housing (12). 8. Ventil nach einem der Ansprüche 1 bis 6,
dadurch gekennzeichnet, daß das Stell­glied (50) ein Kolben ist.8. Valve according to one of claims 1 to 6,
characterized in that the actuator (50) is a piston. 9. Ventil nach Anspruch 8,
dadurch gekennzeichnet, daß das Stell­glied (50) ein Differentialkolben ist.9. Valve according to claim 8,
characterized in that the actuator (50) is a differential piston. 10. Ventil nach einem der Ansprüche 1 bis 6,
dadurch gekennzeichnet, daß das Stell­glied (50) eine Membran ist.10. Valve according to one of claims 1 to 6,
characterized in that the actuator (50) is a membrane. 11. Ventil nach einem der Ansprüche 1 bis 10,
dadurch gekennzeichnet, daß das vom Elek­tromagneten (30) bewegbare Ventilteil (36) kolbenartig axial verschiebbar in einer axial durchgehenden Bohrung (74) im Stellglied (50) geführt ist.11. Valve according to one of claims 1 to 10,
characterized in that the valve part (36) movable by the electromagnet (30) is guided in an axially continuous bore (74) in the actuator (50) in a piston-like manner. 12. Ventil nach Anspruch 11,
dadurch gekennzeichnet, daß der Ventil­sitz (42) einen größeren Durchmesser hat als die Bohrung (74) im Stellglied (50).12. Valve according to claim 11,
characterized in that the valve seat (42) has a larger diameter than the bore (74) in the actuator (50).
EP90119905A 1989-10-18 1990-10-17 Solenoid operated valve, especially for motor vehicle antilocking systems Expired - Lifetime EP0423755B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3934771A DE3934771C1 (en) 1989-10-18 1989-10-18
DE3934771 1989-10-18

Publications (3)

Publication Number Publication Date
EP0423755A2 true EP0423755A2 (en) 1991-04-24
EP0423755A3 EP0423755A3 (en) 1991-10-30
EP0423755B1 EP0423755B1 (en) 1994-12-14

Family

ID=6391722

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90119905A Expired - Lifetime EP0423755B1 (en) 1989-10-18 1990-10-17 Solenoid operated valve, especially for motor vehicle antilocking systems

Country Status (7)

Country Link
US (1) US5076538A (en)
EP (1) EP0423755B1 (en)
JP (1) JP3030074B2 (en)
KR (1) KR100230099B1 (en)
BR (1) BR9005229A (en)
DE (2) DE3934771C1 (en)
ES (1) ES2064585T3 (en)

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WO1993007033A1 (en) * 1991-09-30 1993-04-15 Robert Bosch Gmbh Interlocking connection between a magnetic valve and a casing
WO1993019961A1 (en) * 1992-04-04 1993-10-14 Itt Automotive Europe Gmbh Electromagnetic valve, especially for hydraulic brake systems with slip control
WO1993022168A1 (en) * 1992-04-23 1993-11-11 Allied-Signal Inc. Concentric solenoid valve and sump assembly
US5299859A (en) * 1991-11-15 1994-04-05 Allied-Signal Inc. Combination solenoid valve and shuttle valve
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DE4332372A1 (en) * 1993-09-23 1995-03-30 Bosch Gmbh Robert Electromagnetically actuated valve, in particular for slip-controlled hydraulic brake systems in motor vehicles
DE4332368A1 (en) * 1993-09-23 1995-03-30 Bosch Gmbh Robert Electromagnetically actuated valve, in particular for slip-controlled hydraulic brake systems in motor vehicles
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DE4426796A1 (en) * 1994-07-28 1996-02-01 Bosch Gmbh Robert Solenoid valve for vehicle hydraulic anti-skid braking system
DE4433364A1 (en) * 1994-09-20 1996-03-21 Bosch Gmbh Robert Electromagnetically actuated valve, in particular for slip-controlled hydraulic brake systems in motor vehicles
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GB9608703D0 (en) * 1996-04-26 1996-07-03 Lucas Ind Plc Improved electrically operated trigger valve for fuel injection pump
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US6302499B1 (en) * 1999-12-29 2001-10-16 Kelsey-Hayes Company Control valve for a hydraulic control unit of vehicular brake systems
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US7952261B2 (en) 2007-06-29 2011-05-31 Bayer Materialscience Ag Electroactive polymer transducers for sensory feedback applications
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Cited By (30)

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Publication number Priority date Publication date Assignee Title
EP0526839A1 (en) * 1991-07-30 1993-02-10 Sumitomo Electric Industries, Limited Antilock brake control apparatus
US5242216A (en) * 1991-07-30 1993-09-07 Sumitomo Electric Industries, Ltd. Antilock brake control apparatus
WO1993007033A1 (en) * 1991-09-30 1993-04-15 Robert Bosch Gmbh Interlocking connection between a magnetic valve and a casing
US5299859A (en) * 1991-11-15 1994-04-05 Allied-Signal Inc. Combination solenoid valve and shuttle valve
WO1993019961A1 (en) * 1992-04-04 1993-10-14 Itt Automotive Europe Gmbh Electromagnetic valve, especially for hydraulic brake systems with slip control
US5511864A (en) * 1992-04-04 1996-04-30 Itt Automotive Europe Gmbh Electromagnetic valve, in particular for hydraulic braking systems provided with a slip control
WO1993022168A1 (en) * 1992-04-23 1993-11-11 Allied-Signal Inc. Concentric solenoid valve and sump assembly
EP0670445A1 (en) * 1992-10-30 1995-09-06 Nippondenso Co., Ltd. Electromagnetic valve
EP0670445A4 (en) * 1992-10-30 1995-11-02 Nippon Denso Co Electromagnetic valve.
US5556175A (en) * 1992-10-30 1996-09-17 Nippondenso Co., Ltd. Solenoid valve with ball attracted towards seating because of negative pressure
WO1995009098A1 (en) * 1993-09-28 1995-04-06 Itt Automotive Europe Gmbh Hydraulic braking system with skid control
US5887956A (en) * 1993-09-28 1999-03-30 Itt Automotive Europe Gmbh Hydraulic brake system with slip control
GB2284877A (en) * 1993-11-22 1995-06-21 Bosch Gmbh Robert Electromagnetically operated valve
GB2284877B (en) * 1993-11-22 1997-07-23 Bosch Gmbh Robert Elecromagnetically operated valve
WO1996000671A1 (en) * 1994-06-29 1996-01-11 Itt Automotive Europe Gmbh Controlled-slip hydraulic brake system
US6003958A (en) * 1994-06-29 1999-12-21 Itt Manufacturing Enterprises Inc. Hydraulic brake system with slip control
US5975654A (en) * 1994-08-06 1999-11-02 Itt Manufacturing Enterprises Inc. Valve unit, in particular for hydraulic brake systems with antilock and/or wheel-slip control
WO1996005090A1 (en) * 1994-08-06 1996-02-22 Itt Automotive Europe Gmbh Valve device, in particular for hydraulic brake systems with abs or drive-slip control, and a method of adjusting a valve device
FR2723712A1 (en) * 1994-08-18 1996-02-23 Bosch Gmbh Robert ELECTROMAGNETICALLY CONTROLLED VALVE FOR HYDRAULIC BRAKING SYSTEMS WITH THE ADJUSTMENT OF THE SKATING OF MOTOR VEHICLES.
US6086164A (en) * 1994-10-27 2000-07-11 Robert Bosch Gmbh Magnet valve with pressure limitation for slip-controlled motor vehicle brake systems
WO1996013414A1 (en) * 1994-10-27 1996-05-09 Robert Bosch Gmbh Magnetic valve with pressure limitation for controlled-slip motor vehicle braking systems
US6032692A (en) * 1995-08-12 2000-03-07 Itt Manufacturing Enterprises Inc. Electromagnetic valve, in particular for hydraulic motor vehicle braking systems with wheel slip regulation
WO1997007002A1 (en) * 1995-08-12 1997-02-27 Itt Automotive Europe Gmbh Electromagnetic valve, in particular for hydraulic motor vehicle braking systems with wheel slip regulation
WO1997028998A1 (en) * 1996-02-07 1997-08-14 Robert Bosch Gmbh Electromagnetically-operated valve, especially for vehicle hydraulic brake systems
WO1997046433A1 (en) * 1996-06-01 1997-12-11 Lucas Industries Public Limited Company Improvements in hydraulic control valve assemblies for hydraulic braking systems
AT502512B1 (en) * 2005-11-15 2007-04-15 Hoerbiger Valvetec Gmbh gas metering valve
WO2011079980A1 (en) * 2009-12-28 2011-07-07 Robert Bosch Gmbh Solenoid valve
CN102686463A (en) * 2009-12-28 2012-09-19 罗伯特·博世有限公司 Solenoid valve
US9074701B2 (en) 2009-12-28 2015-07-07 Robert Bosch Gmbh Solenoid valve
CN102686463B (en) * 2009-12-28 2015-09-02 罗伯特·博世有限公司 Electromagnetic valve

Also Published As

Publication number Publication date
DE3934771C1 (en) 1991-03-28
KR910008321A (en) 1991-05-31
KR100230099B1 (en) 1999-11-15
US5076538A (en) 1991-12-31
BR9005229A (en) 1991-09-17
JPH03134385A (en) 1991-06-07
DE59008007D1 (en) 1995-01-26
ES2064585T3 (en) 1995-02-01
EP0423755B1 (en) 1994-12-14
EP0423755A3 (en) 1991-10-30
JP3030074B2 (en) 2000-04-10

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